Exhaust manifold device



July 15, 1969 c. R. FLINT 3,

EXHAUST MANIFOLD DEVICE Y Filed May 5, 19s? 2 Sheets-Shet 1 0207 165 $122k 29 aAw dwmwgw s,

Tlited 3,455,106 EXHAUST MANIFOLD DEVICE Charles R. Flint, Clear-Ex Corporation, 402 Clay St, La Porte, Ind. 46350 Filed May 5, 1967, Ser. No. 636,415 Int. Cl. F0111 3/10 US. Cl. 6030 12 Claims ABSTRACT OF THE DISCLOSURE During the operation of an internal combustion engine, gases resulting from an explosion in a cylinder of the engine are expelled from the cylinder in an initial high pressure pulse or wave. By experimentation it has been proven that the initial high pressure wave or pulse has a relatively long duration and is followed by a series of alternating low and high pressure pulses of shorter duration. Of course, a series of the alternating high and low pressure waves is formed in the exhaust manifold each time an exhaust valve for any one of a plurality of engine cylinders is opened. During the high pressure pulses, com bustion products or exhaust gases are expelled from the cylinders of the engine. However, during the low pres sure pulses, the mainly noncombustible exhaust gases are drawn back into the cylinders. These exhaust gases are often retained in the cylinder when the exhaust valve closes and the gases substantially dilute the air-fuel mixture for the next cycle of operation. This dilution of the air-fuel mixture with largely noncombustible exhaust gases significantly retards combustion within the cylinder on the succeeding power stroke.

The quantity of largely noncombustible exhaust gases which are drawn into the cylinder during a low pressure pulse or wave can be substantially reduced by inducting air into the exhaust manifold during the low pressure pulse. The induced air increases the power and efliciency of the engine through the two-fold effect of promotlng combustion and reducing the quantity of noncombustible exhaust gases in the cylinder. Air is commonly induced into the exhaust manifold by using a spring controlled check valve assembly. The check valve assembly is opened during the low pressure pulse, which has a relatively short duration, to enable air to fiow into the exhaust manifold. The check valve assembly is closed during the high pressure pulse to prevent exhaust gases from flowing through the check valve assembly.

The use of these prior art assemblies substantially increases the efiiciency of an engine. However, the prior art assemblies all include spring loaded or actuated check valves which are not immediately responsive to changes in pressure due to inertia of the valve and the spring. The necessity of a highly sensitive check valve assembly becomes quite apparent upon considering that a four cylinder, four stroke, engine which is operating at 1,800 r.p.m. has fifteen openings and closings per second of the exhaust valve associated with each cylinder. Therefore, the four cylinder engine sets up sixty series of high and low pressure pulses in the exhaust manifold per second. Since each series of pulses includes a plurality of high and low pressure peaks and valleys, the check valve assembly must operate far in excess of sixty times a second when the engine is running at 1,800 r.p.m. Of course, the

3,455,16 Patented July 15, 1969 necessity for rapid operation of the check valve is increased by the relatively short duration of the low pressure pulses compared to the high pressure pulses. The lack of responsiveness or sensitivity of the prior art valve assemblies results in a hunting or floating of the check valve rather than a positive opening and closing of the valve, as is required to maximize engine efficiency.

Therefore, it is an object of this invention to provide an exhaust manifold device which overcomes the aforementioned disadvantages of prior art constructions. Specifically, it is an object of this invention to provide an exhaust manifold device having a highly senstitive check valve assembly for controlling induction of air into an exhaust manifold of an engine.

Another object of this invention is to provide an exhaust manifold device which promotes a rapid flow of air into an exhaust manifold.

These and other objects and features of the invention will become more apparent upon a consideration of the following detailed description, taken in connection with the accompanying drawings wherein:

FIG. 1 is a perspective view of a preferred embodiment of the exhaust manifold device shown mounted on an exhaust manifold of an engine;

FIG. 2 is a partial sectional view illustrating the structure of the exhaust manifold device of FIG. 1;

FIG. 3 is a perspective view illustrating the exhaust manifold device of FIG. 1 with a cap or cover removed;

FIG. 4 is an enlarged sectional view illustrating the structure of a valve chamber and check valve assembly used in the exhaust manifold device, the check valve assembly being shown in an open position;

FIG. 5 is an enlarged exploded perspective view illustrating the shape and interrelationship of the components of the valve assembly of FIG. 4;

FIG. 6 is an enlarged plan view, taken along the line 66 of FIG. 4, illustrating the structure of a storage or cavity washer used in the valve assembly;

FIG. 7 is an enlarged sectional view, similar to FIG. 4, showing the check valve assembly in a closed position;

FIG. 8 is an enlarged cross-sectional view, similar to FIG. 4, of a second embodiment of the invention; and

FIG. 9 is an enlarged plan view, taken along the line 99 of FIG. 8 and similar to FIG. 6, illustrating the structure of a washer used in the second embodiment of the invention.

Referring now to FIG. 1 in greater detail, an exhaust manifold device 20 is shown mounted on an exhaust manifold 22 of an internal combustion engine. The exhaust manifold device 20 can advantageously be used with either two or four cycle or stroke engines having any desired number of cylinders. The exhaust manifold device 20 includes a head section 24 which is supported on a stem section 26. The stem section 26 includes heat exchanger 28 having a threaded end portion 30 which is received in a tap hole in the exhaust manifold 22. The heat exchanger 28 includes a plurality of fins 32 which dissipate heat conducted from the manifold 22 to prevent the head section 24 from being heated to a relatively high temperature and damaging a check valve assembly located in the head section. A neck or tube 36 is connected to the heat exchanger 28 by a threaded mounting nut 38. As is perhaps best seen in FIG. 2, the nut 38 engages a packing gland or ring 42 which is connected to the neck 36 to secure the head section 24 to the heat exchanger 28.

Referring now to FIGS. 2 and 3, it can be seen that the head section 24 includes a cap or cover 46, which is retained on a radially and axially outwardly flaring base wall 48 by a plurality of tabs or fingers 50. The cap 46 has a substantially larger diameter than the base wall 48 so that ambient or surrounding air can be drawn into an outer chamber 54 through a passage 56 extending between a downwardly extending rim or flange 58 of the cap 46, and an upwardly extending flange or rim 60 of the base wall 48. A pair of opposite arcuate recesses 62 are provided in the upwardly extending flange 60 to enable the air to enter the outer chamber 54.

A check valve assembly 66 is mounted within the outer chamber 54 on a connecter sleeve 68 which is fixedly secured to the neck 36. The check valve assembly 66 enables ambient air to flow from the chamber 54 through a central passage 70 in the neck 36 into the manifold 22 through a passage 74 in the heat exchanger 28 when a low pressure wave or pulse is present in the exhaust manifold 22. When a high pressure wave or pulse is present in the exhaust manifold 22, the check valve assembly 66 is closed by fluid pressure transmitted from the exhaust manifold 22 through gases in the passages 74 and 70. Thus, the check valve 66 enables ambient air to flow into the exhaust manifold during low pressure waves to reduce the amount of exhaust gases which are drawn back into a cylinder of an engine. The check valve 66 is closed during the high pressure pulses to prevent exhaust gases from being discharged out of the exhaust manifold device 20.

The construction of the check valve assembly 66 is illustrated in greater detail in FIG. 4. The check valve assembly 66 includes a generally cylindrical side wall with a radially inwardly extending flange 82 located at an inner end of the side wall 80. The flange 82 is positioned in abutting engagement with a rim 84 of the base wall 48. The flange 82 and the rim 84 are fixedly secured to the connector 68 by a radially outwardly extending flange or end portion 86 of the connector 68. An end wall or closure 90 is fixedly mounted at an outer end of the side wall 80. The end wall 90 and side wall 80 define a valve chamber 94 in which a valve structure 96 is loosely or freely mounted for independent movement within the chamber 94.

The valve structure 96 is shown in an exploded or separated relationship in FIG. 5. The valve structure 96 is advantageously formed of rigid commercially available heat-resistant asbestos held together by a polymeric binding. The valve structure 96 includes a rigid generally circular valve member or plate 100 having an outer transversely extending surface 102 which engages an annular inwardly projecting valve seat 104 formed on an inner portion of the end wall 90. The valve seat 104 extends around or circumscribes a central aperture 106 in the end wall 90. When the valve assembly 66 is open (as shown in FIG. 4), air is conducted into the valve chamber 94 through the aperture 106. When the valve assembly 66 is closed (as shown in FIG. 7), the upper surface 102 of the valve member 100 engages the valve seat 104 to block or seal the aperture 106.

Referring again to FIG. 5, it should be noted that an uneven number of chordal flats 110 (in the embodiment shown, three) are formed in a radially outer edge portion of the valve member 100. The flats 110 enable air to readily flow between the outer edge portion of the valve member 100 and the side wall 80 when the valve member is in an open position (shown in FIG. 4). By experimentation it has been determined that an odd number of flats leads to the greatest flow of air through the open valve assembly 66. It is believed that an even number of flats results in a crossflow of air around the valve member 100. However, regardless of the reason, the use of an uneven number of flats promotes the flow of air, while it has been found that the use of an even number of flats tends to retard the flow of air.

An outer washer or annular member 114 is positioned immediately inwardly of the valve member 100. The outer washer 114 is generally circular in shape and includes a circular central axially extending aperture or hole 116 defined by a side wall or surface 118. When the valve assembly 66 is open the washer 114 is positioned with an outer transversely extending surface 120 in abutting juxtaposition with an inner surface of the valve member 100. Through extensive testing it has been determined that the outer washer 114 promotes a rapid movement of the valve member 100 from the open position of FIG. 4 to the closed position of FIG. 7. It is believed that the washer 114 promotes this rapid movement by directing and at least partially containing a high pressure wave or pulse from the exhaust manifold 22 with the side wall 118 of the aperture 116. The pulse or pressure wave enters the valve chamber and is retained from spreading or mushrooming outwardly against the inner surface of the valve member 100 by the axially extending side wall 118. Thus, the pressure pulse is both contained and directed by the side wall 118 against the inner surface of the valve member 100. An even number of chordal flats 12.2 are provided on an outer edge portion of the washer 114 for cooperation with an air cross or spacer member 126 in a manner to be explained in greater detail subsequently.

Continuing with reference to FIG. 5, the air cross or space 126 includes a plurality of radially extending leg members 130 having an outer surface 132 which i. positioned in abutting engagement with an inner surface of the washer 114. The transversely extending legs 130 space the outer washer 114 from an intermediate washer 136 to enable air to flow around the chordal flats 122 of the Washer 114 between the leg sections 130 of the spacer 126 and through a circular central aperture 138 in the intermediate washer 136. As previously mentioned, an even number of flats 122, in the embodiment shown, six are formed on the washer 114. It should be noted that the number of flats exceeds the number of leg sections 130 of the spacer 126. This particular combination of flats and leg sections has been found by experimentation to promote the flow of air around the washer 114 and spacer 126 and through the aperture 138 in the washer 136. It is believed that the larger even number of flats 122 on the outer washer 114 breaks up the space between the leg sections 130 into a plurality of channels through which the air can readily flow.

An air storage or cavity washer 142 is positioned with an outer surface 144 in juxtaposition with an inner surface of the washer 136. As perhaps can best be seen by a comparison of FIGS. 4, 5 and 6, the storage washer 142 includes a plurality of radially extending generally U- shaped outer recesses or cavities 148. The recesses 148 extend inwardly from the outer surface 144 of the storage washer 142 for an axial distance which is slightly greater than the axial thickness of the washer. A second group or plurality of recesses 150 extend axially inwardly from a lower surface 154 of the Washer 142. The recesses 150 extend radially outwardly in much the same manner as do the recesses 148. The recesses 150 also extend for more than half the axial thickness of the washer 142. As can be clearly seen in FIG. 6, the recesses 148 and 150 are offset relative to each other to strengthen the storage washer 142. By reference to FIGS. 4 and 5 it can be seen that the washer 142 is beveled by oppositely sloping surfaces 158 and 160 at its radially outer edge. The intermediate washer 136 and an inner washer 164 extend radially outwardly of the sloping surfaces 158 and 160 to form a generally annular cavity 168 (see FIG. 4) between the intermediate washer 136, the beveled surfaces 158 and 160 of the storage washer 142, and the inner washer 164. The intermediate washer 136 and the inner washer 164 also block the outwardly and inwardly opening cavities or recesses 148 and 150.

When a high pressure pulse or wave passes through the exhaust manifold 22, pressure is transmitted by gases in the passages 74 and 70 (see FIG. 2) to the valve chamber 94. This pressure compresses air in the radially extending cavities 148 and 150 of the storage washer 142. Air is also compressed in the annular cavity 168 formed between the intermediate washer 136 and the inner washer 164. When the high pressure pulse or wave passes through the manifold 22 and is followed by a low pressure pulse or wave, the air in the cavities 148 and 150 flows through the passage 70 and into the manifold 22. The compressed air in the annular cavity 168 then flows through the radial cavities 148, 150, which are in fluid communication with the annular cavity 168, into the passage 70. In this manner the storage washer 148 holds or stores air during the high pressure pulses in the manifold so that air can be immediately induced into the manifold from the valve chamber when a low pressure pulse passes through the manifold.

The storage washer 142, the intermediate washer 138 and inner washer 164 could be eliminated from the valve structure 96. However, if they were omitted, air would not be compressed and stored to provide an immediate charge in response to the formation of a low pressure pulse or wave in the manifold 22. As was previously explained, these pulses or waves occur with extreme rapidity and therefore air must be inducted into the manifold 22 as quickly as possible. The air storage washer 142 promotes the rapid induction of air into the manifold 22 and is therefore included in the preferred embodiment of the invention.

As is perhaps best seen by a comparison of FIGS. 4 and 7, the components of the valve structure 96 are freely or loosely positioned in a substantially coaxial relationship in the valve chamber 94. The radially outer surfaces of the components of the valve structure 96 are spaced apart from the wall 80 to enable the components to move separately and independently relative to the wall 80 without interference. The components are normally positioned against flange 86 of the connector '68 with the valve structure 96 in an open position. The valve structure 96 remains open until the engine is started. Im mediately upon starting the engine high and low pressure pulses cause the valve structure to reverberate or move rapidly from the open position of FIG. 4 to the closed position of FIG. 7. The rapid positive closing of the valve structure 96 results from a transmission of high pressure pulses against the valve member 100 from the manifold 22 as a high pressure wave or charge of exhaust gases passes through the manifold. Immediately upon passing of the high pressure wave, a low pressure wave of a relatively short duration is formed in the manifold 22. The valve member 100 is then snapped to the open position by the pressure of air against an outer surface of the valve member.

It should be noted that the movement of the valve member from the closed position of FIG. 7 to its normal open position of FIG. 4 is facilitated by gravity which tends to pull the valve member 100 from the closed position to the open position. The movement of the valve member 100 from the closed position to the open position is also facilitated by a generally cylindrical recess or chamber 180 (see FIG. 7) defined by the valve seat 104 and a radially extending transverse inner surface 182 of the end wall 90. As the valve member 100 is moved from the open position to the closed position, air is compressed against the radial surface 182 in the compression chamber or recess 180. The compressed air tends to force or urge the valve member 100 toward the open position so that the valve assembly 66 opens immediately upon the formation of a low pressure wave within the manifold 22. Thus, there are three forces tending to urge the valve member from the closed position of FIG. 7 to the open position of FIG. 4 when a low pressure wave or pulse is present in the manifold 22. These forces are the pressure of the ambient air through the aperture 106 on the outer surface of the valve member 100, the pressure of the compressed air in the chamber 180, and the force of gravity acting to pull the valve member 100 inwardly or downwardly. In fact, the compressed air in the chamber 180, and the force of gravity on the valve member 100 tend to make the valve member open slightly before the high pressure wave has completely passed, so that a maximum amount of air can be inducted into the manifold during a relatively large portion of the comparatively short duration of the low pressure pulse or wave which follows the high pressure pulse or wave.

While the three forces which were previously mentioned tend to open valve structure 96, it should be noted that all but one of the forces are dissipated before the subsequent high pressure wave or pulse occurs in the manifold 22. Thus, the force of the ambient air or atmosphere on the outer surface of the valve is dissipated when the high pressure wave begins, since there is no longer a pressure differential tending to open the valve assembly 66 between the ambient air and the exhaust gases in the manifold. The compressed air in the chamber 180 is released as soon as the valve member 100 moves to the open position. Only the force of gravity acting on the valve member 100 remains to retard the motion of the valve member from the open position of FIG. 4 to the closed position of FIG. 7 when a high pressure wave begins to form in the manifold 22. Since the valve member 100 is made of a light weight asbestos compound bound together with polymeric substance, the force of gravity is readily overcome by fluid pressure transmitted from the manifold 22 to quickly and positively close the valve during the high pressure pulse. Thus, there are several cumulative forces acting on the valve member 100 to move the valve member from the closed position to the open position so that air can be inducted into the manifold 22 during the relatively short low pressure pulse which follows a high pressure pulse. Only one of these forces, that is gravity, is present after the low pressure pulse passes so that the valve member can move quickly to the closed position when the high pressure pulse is present in the manifold 22.

To heighten the readers understanding of the invention, a second embodiment has been shown in FIGS. 8 and 9. The embodiment of FIGS. 8 and 9 is substantially the same as the embodiment illustrated in considerable detail in FIGS. 17, and similar components have been designated in FIGS. 8 and 9 with numerals similar to those used in connection with the embodiment of FIGS. 1-7. To avoid confusion, the similar components of FIGS. 8 and 9 have been designated with numerals having the suflix a.

As can be seen from a comparison of FIGS. 4 and 8, valve structure 96a is substantitally similar to valve structure 96. However, valve structure 96a has a storage washer 200 which is different from the storage washer 142 of the embodiment set forth in FIGS. 1-7. The storage washer 200 includes a central aperture or hole 202 defined by oppositely radially outwardly sloping surfaces 204, 206 forming a bevel in the center of the washer 200 rather than at the outer edge as is the case with the storage washer 142. In addition, the storage Washer 200 does not have radially extending recesses, as does the storage washer 142.

The sloping bevel surfaces 204, 206 have been found to be advantageous in opening and closing the valve structure 96a. It is believed that the advantageous structure of the storage Washer 200 results from a compression of air between the upper beveled surface 204 and the washer 136a when the valve structure 96a is moved to a closed position. Of course, this compressed air tends to move the storage washer 200 downwardly to the open position of FIG. 8 when a low pressure pulse passes through the exhaust manifold. Conversely, the inner surface 206 is believed to be engaged by high pressure gases when a high pressure pulse or wave is present in the exhaust manifold, to snap the valve structure 96a closed.

The operation of the exhaust manifold device 10, constructed and illustrated in the embodiment of FIGS. 17 and the embodiment of FIGS. 8 and 9, will be largely apparent from the foregoing description. However, it should be noted that the valve structure 96 is extremely rapid and positive in its opening and closing. This rapid, positive opening and closing of the valve structure 96 results from the loosely mounted combinations of components which are free to move independently relative to the side walls of the valve chamber 94 from an open position to a closed position. The closing of the valve structure 96 is further facilitated by the outer washer 114 which contains and directs a high-pressure fluid pulse against the valve member 100 to close the valve member. The valve member in an open position at the beginning of a high pressure wave in the exhaust manifold. The valve structure 96 will be opened under the combined cumulative pressure of atmosphere on the outer surface of the valve member 100, gravity, and compressed air within the chamber 180 at the beginning of a relatively short, lowpressure wave in the exhaust manifold 22. Thus, a plurality of cumulative forces tend to quickly open the valve structure 96 so that air can be induced into the manifold 22 on the occurrence of a low pressure pulse in the manifold.

A preferred embodiment of the invention has been shown, utilizing a particular combination of valve member, washer, and spacer. This particular combination was arrived at through extensive experimentation and provides a relatively fast acting valve structure through which air can pass quickly into the manifold 22. Several theories as to the reasons for the particularly advantageous action of the valve structure 96 have been set forth herein. While these theories apparently conform with the facts and are believed to be correct, it is not desired to be limited to any particular theory of operation. Any theory of the flow of air in the valve assembly, due to the extremely rapid formation of high and low pressure waves in the manifold 22, must of necessity be based in part on conjecture. It should also be understood that many, many different combinations of components have been used experimentally in the valve structure 96. The particular components can be varied greatly in configuration and the valve assembly 66 will still operate. However, the illustrated valve assembly is preferred due to its rapidity of action and the ease with which air is conducted through the valve assembly. Therefore, while particular embodiments of the invention have been shown, it should be understood that the invention is not limited thereto since many modifications may be made; and it is contemplated to cover by the appended claims any such modifications as fall within the true spirit and scope of the invention.

What is claimed is:

1. An assembly for mounting on an exhaust manifold of an engine to induct air into the exhaust manifold, said assembly comprising: a stern section for connection to the exhaust manifold of the engine, said stern section including a longitudinally extending stern passage; a wall means connected to said stem section to at least partially define a valve chamber, said wall means including inner aperture means to provide fluid communication between the stem passage and the valve chamber; a valve seat defined by said wall means, said valve seat circumscribing an outer aperture means in said wall means to enable air to flow into said valve chamber; a valve member loosely positioned in the valve chamber for free movement relative to said wall means, said valve member being normally spaced apart from said valve seat in an open position to enable air to flow through the valve chamber and stem passage into the exhaust manifold, said valve member being moved to a closed position by fluid pressure transmitted from the exhaust manifold, and a washer member loosely positioned in the valve chamber in juxtaposition with an inner surface of said valve member for free movement relative to said wall means, said washer member defining an aperature means into which fluid pressure pulses are transmitted from the exhaust manifold, said washer member at least partially containing the fluid pressure pulses to direct the fluid pressure pulses against said valve member to move the valve member to the closed position in which said valve member is in engagement with said valve seat to block said outer aperture means when gas in the exhaust manifold is at a higher pressure than the surrounding atmosphere.

2. An assembly as set forth in claim 1 wherein: said wall means includes a transverse surface extending between said valve seat and the outer aperture means, said transverse surface being spaced outwardly of said valve member when said valve member is in engagement with said valve seat to at least partially define a compression chamber in which gases arecompressed when said valve member is moved to the closed position by fluid pressure transmitted from the exhaust manifold, said valve member being urged toward the open position by gases compressed in the compression chamber to provide an immediate movement of the valve member from the closed position to the open position.

3. An assembly as set forth in claim 1 wherein: said stem section includes a finned heat exchanger means for retarding heat transfer between an exhaust manifold and said wall means and valve member.

4. An assembly as set forth in claim 1 wherein: said valve member and said valve seat have a generally circular configuration with an odd number of chordal flats formed in an outer edge portion of said valve member to facilitate the flow of air around said valve member when said valve member is in the open position.

5. An assembly as set forth in claim 1, further including: a spacer member loosely positioned in said valve chamber for free movement relative to said wall means with an outer surface of said spacer member in juxtaposition with an inner surface of said washer member,'said spacer member having a generally cross-shaped configuration to form a plurality of passages through which air can flow when said valve member is in the open position.

6. An assembly as set forth in claim 1, wherein: said washer member has a generally circular configuration with an even number of chordal flats formed in an outer edge portion to facilitate the flow of air through the passages formed by said spacer member.

7. An assembly for mounting on an exhaust manifold of an engine to induct air into the exhaust manifold, said assembly comprising: a stem section for connection to the exhaust manifold of the engine, said stem section including a longitudinally extending stern passage; a wall means connected to said stem section to at least partially define a valve chamber, said wall means including inner aperture means to provide fluid communication between the stem passage and the valve chamber; a

valve seat defined by said wall means, said valve seat circumscribing an outer aperture means in said wall means to enable air to flow into said valve chamber; and a valve member loosely positioned in the valve chamber for free movement relative to said wall means, said valve member being normally spaced apart from said valve seat in an open position to enable air to flow through the valve chamber and stem passage into the exhaust manifold, said valve member being moved to a closed position by fluid pressure transmitted from the exhaust manifold, said valve member being in engagement with said valve seat in said closed position: to block said outer aperture means when gas in the exhaust manifold is at a higher pressure thanthe surrounding atmos-, phere, and first andsecond washer members loosely positioned in said valve chamber inwardly of said valve memher; and a storage washer loosely positioned, in said valve chamber intermediate said first andzsecond washer members, said storage washer including a first group of recesses extending inwardly from an outer transverse surface of said storage washer anda second group of recesses extending outwardly from an inner transverse surface of said storage washer, said first group of recesses being blocked by said first washer member and said second group of recesses being blocked by said second washer member to provide a plurality of storage cavities in which air is compressed as said valve member is moved to the closed position and from which the compressed air flows when said valve member the open position.

8. An assembly as set forth in claim 7 wherein: a radially outer edge portion of said storage washer is beveled and said first and second washer members extend radially outwardly on opposite sides of the bevel in said storage washer to provide an annular cavity connected in fluid communication with said plurality of cavities to increase the quantity of air which is compressed as said valve member is moved to the closed position.

9. An assembly as set forth in claim 7, wherein: said first group of cavities extends through a major portion of an axial dimension of said storage washer and said second group of cavities are offset relative to said first group of cavities and extend through a major portion of said storage washer to provide cavities having a relatively large volume in a relatively strong storage washer.

10. An assembly for mounting on an exhaust manifold of an engine to induct air into the exhaust manifold, said assembly comprising: wall means defining a valve chamber having an outer aperture means opening to atmospheric pressure through which air enters the valve chamber and an inner aperture means through which air leaves the valve chamber and flows into the exhaust manifold; a valve member loosely positioned in said valve chamber, said valve member being freely movable from a normal first position spaced apart from said outer aperture means under influence of gravity and with its outer surface subject to atmospheric pressure to a second position blocking said outer aperture means by a high pressure fluid pulse from the manifold; and a compression chamber means formed in said wall means outwardly of said valve member in which air is compressed by movement of said valve member to the second position, said valve member being detached from said wall means for free movement from the second position to the first position upon formation of a low pressure pulse in the exhaust manifold, said valve member being moved from the secis moved to ond position to the first position when the low pressure pulse formed by the combined effects of gravity and of atmospheric pressure against an outer surface of the valve member and the air compressed in said compression chamber, said valve member when in said second position enabling air to flow through said outer aperture means into the exhaust manifold.

11. An assembly as set forth in claim 10, further including: air storage means loosely positioned in said valve chamber inwardly of said valve member, said air storage means including a plurality of chambers in which air is compressed when a high pressure pulse is formed in the exhaust manifold and from which the compressed air flows when a low pressure pulse is formed in the exhaust manifold.

12. An assembly as set forth in claim 10, further including a washer member loosely positioned in the valve chamber in juxtaposition with an inner surface of said valve member for free movement relative to said wall means, said washer member defining an aperature means into which fluid pressure pulses are transmitted from the exhaust manifold, said washer member at least partially containing the fluid pressure pulses to direct the fluid pressure pulses against said valve member to move the valve member to the closed position.

References Cited UNITED STATES PATENTS 

